Wafering machine and method



Jan, 21, 1969 F. N. REECE WAFERING MACHINE AND METHOD Filed March 51, 1966 Sheet INVENTOR F/oyd Reece Jan. 21, 1969 F. N. REECE 3,422,747

WAFERING MACHINE AND METHOD Filed March 31., 1966 Sheet 7 3 of 5 I. A .3a0 94 H 6 F g 55 l M147 .50 [Q0 2 1 [I' 44 I 42 I e (95 95 4 44 5 /00 InHM, l u

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INVENTOR Floyd N. Reece United States Patent 20 Claims ABSTRACT OF THEDISCLOSURE A method and apparatus for wafering materials such as hay orthe like. A rotary drum provided with a plurality of outwardlyextending, peripherally spaced projections is advanced intermittentlywhereby a portion of the material is pushed in one direction by aprojection to compress the material. After advancement of the drum onestep, a hydraulic ram is pivoted into the path of the material and isadvanced in the opposite direction to condense t-he material into awafer. The ram is then withdrawn and pivoted out of the path of theprojection whereupon the next increment of the step by step advancementof the drum is carried out.

This invention relates to the condensation of compressible materialsinto relatively small wafers by the application of compressive forces,the primary object being to attain substantial uniformity in densitynotwithstanding wide differences in the condition of the materials beingwafered not only from the standpoint of moisture content but from thestandpoint of other inherent characteristics such as its fibrous nature,comminuted state and ability to fuse in response to compressive forces.

It is one of the most important objects of the present invention toprovide a system of wafering that is especially adapted for handling haysuch as alfalfa and other crops, especially those used for animal feed,utilizing compressive forces in a manner to cause a rather largepercentage of the available energy in the initial compaction to the endthat a minimum amount of work is required in the final step ofapplication of high compressive forces.

It is another object of my present invention to wafer crops by gatheringtogether the loose material and, at the same time, compress it into arelatively compact mass prior to the final high pressure step with thelatter acting upon the precompressed mass continuously until apredetermined pressure is reached, to the end that air is expelledtherefrom and fusion takes place with uniform density, rapidity, andminimum energy.

A further important object of the instant invention is to carry out theaforementioned aims through use of novel apparatus capable ofwithstanding the forces applied to the material by virtue of the way inwhich precompression takes place in one direction, the precompressedmaterial is shifted along an arcuate path of travel, and the final stageof compression takes place linearly through use of a hydraulic pistonand cylinder assembly operating tangentially to the aforementioned path.

In the drawings:

FIGURE 1 is a fragmentary, side elevational view of a watering machinemade pursuant to my present invention and capable of carrying out thenovel method hereinafter described;

FIGURE 2 is a fragmentary, elevational view showing the opposite side ofthe machine;

FIGURE 3 is a substantially central, vertical, crosssectional viewthrough the machine;

FIGURE 4 is a view similar to FIG. 3 but illustrating certain componentparts in a different position;

FIGURE 5 is an enlarged, fragmentary, cross-sectional view taken on line5--5 of FIGURE 1;

FIGURE 6 is a fragmentary, enlarged, cross-sectional view taken on line6-6 of FIGURE 1;

FIGURE 7 is an enlarged, fragmentary, cross-sectional view taken on line77 of FIGURE 1;

FIGURE 8 is an enlarged, fragmentary, cross-sectional view taken on line8-8 of FIGURE 2;

FIGURE 9 is a detailed, cross-sectional view taken on line 9-9 of FIGURE2; and

FIGURE 10 is a diagrammatical view illustrating the electrical systemand components in conjunction with certain of the associated mechanicalparts.

The 'wafering machine of the present invention, broadly designated bythe numeral 20, may be stationary or it may be supported on a mobileframe (not shown) which is coupled with a tractor for towing machine 20through a field. The main body of machine 20 comprises a pair of spaced,parallel, vertical walls 22, each of which includes an upper wallsect-ion 24 having an integral, rearward extension 26 and a lower wallsection 28 which is connected to the mobile frame by legs 30. Wallextensions 26 are interconnected near the rear of machine 20 by acrossbeam 32, there being a cross member 34 simila-rily interconnectingupper wall sections 24 near the front of machine 20 (FIG. 3).

Referring to FIG. 2, each upper wall section 24 has a drum support plate36 mounted thereon, and plates 36 rotatably receive a drum shaft 38which carries a rotor or drum 40 between and partially within walls 22.Drum 40 is hollow and presents a peripheral rim 41 which travels inclosely spaced relationship to upper wall sections 24 as shown in FIG.6. A plurality of lugs 42 extend outwardly from drum 40 at itsperiphery, there being five such lugs in the machine illustrated,whereby to present five elongated, circumferential, material-receivingcavities 44a-e. Each lug 42 is split to present a pair of side-bysideadvancing anvil faces 46 and corresponding rear faces 47 which define aslot 48 therebetween. Each rear face 47 is backed by a pair of spacedbraces 50 secured to rim 41 of drum 40 and presenting a backup receivingrecess 51 therebetween.

An arcuate plate 52 spans the distance between walls 22 and is securedto the latter adjacent the instantaneous lower front quadrant of drum40. Plate 52 is concentric with the drum about shaft 38 and is spacedfrom drum 40 so that lugs 42 travel in close relationship to theproximal surface of plate 52 (FIG. 6). A knife 54, having a steppedcutting edge 56, is welded to arcuate plate 52 and extendslongitudinally thereof in alignment with slots 48 of lugs 42. Knife 54is in end-to-end relationship with a divider 58 welded to arcuate plate52 and extending over the latter to present a ram guide 66).

A pair of rectangular backup elements 62 extend through slits in plate52 and are pivotally mounted on the backup shaft 64 which is securedbetween walls 22 and disposed between the upper and lower rails 66 ofcross member 34. With reference to FIG. 5, backup elements 62 are heldin spaced relationship by links 68 and maintained in alignment withslots 51 of lugs 42 by spacers 70 secured between rails 66 of crossmember 34. One of the backup elements 62 has a forwardly extending arm71, the outermost end thereof being interconnected by a tension spring72 to the outer end of a plate 74 extending forwardly from lower wallsection 28. Spring 72 yieldably biases backup elements 62 against rim 41of drum 40, the upper rear corners of backup elements 62 being bevelledto present complemental drum engaging surfaces 76.

A supply hopper 78 is mounted adjacent drum 40 to communicate withproximal cavities 44 and includes a pair of side walls 80 extendingabove and coplanar with corresponding upper wall sections 26. A rearplate 82 spans the distance between side walls 80 and presents anopening 84 therebelow to permit travel of lugs 42 by hopper 78. Theforward portions of side walls 80 are interconnected by a front plate86, the latter defining an opening 87 therebelow which permits swingabletravel of a generally triangular feeder 88.

Feeder 88 is pivotally mounted between side walls 80 by a pivot pin 90which swingably receives the arcuate gate member 92 of feeder 88. Anarcuate shelf 94 extends generally forwardly of gate member 92 andswings in an are directly beneath scraper edge 96 presented by frontplate 86. A bracket 98 is secured to gate member 92 adjacent pivot pin90 and is interconnected with shelf 94 by a brace 100. Hopper 78 andfeeder 88 cooperate to form a material-loading station for cavities 44.

Four horizontal shafts are rotatably supported between lower wallsections 28 and include, beginning at the front of the machine, a feedershaft 102, a cam shaft 104, a planetary shaft 106, and a clutch shaft108. Referring to FIG. 2, which shows one side of wafering machine 20,clutch shaft 108 has a clutch sprocket .110 rotatable thereon, thesprocket being rotated by acting in cooperation with shaft 108 through aclutch assembly 112. An outer sprocket 114 is secured to planetary shaft106 for rotation therewith and is interconnected with clutch sprocket110 by a chain 116, the latter also being trained under an idlersprocket 118. A hydraulic cam wheel 120 and a brake cam wheel 122 spacedinwardly thereof are coupled for rotation with cam shaft 104, as shownin FIG. 9. Cam wheels 120 and 122 are provided with correspondingcamming ridges 124 and 126 which will be explained in detail below.

Next, referring to FIG. 1 which shows the other side of wafering machine20, clutch shaft 108 has a drive wheel 128 rigidly secured thereto, thelatter being connected by a drive belt 130 for rotation by a power wheel132 of a prime mover (not shown) mounted on the mobile frame carryingmachine 20. Planetary shaft 106 is rotatably journalled into a bearingmount 134 which is. secured on the top surface of platform 136, therebeing a drive sprocket 138 spaced inwardly of bearing mount 134 onplanetary shaft 106 (FIG. 7) and coupled by chain 139 to drum sprocket141 for driving the drum.

Cam shaft 104 is provided with a cam sprocket 140 rotatable therewith,while feeder shaft .102 is provided with a rigidly secured reducingsprocket 142, the latter being coupled to cam sprocket 140 by a chain144. The radius of reducing sprocket 142 is one-fourth that of camsprocket 140, whereby four 360 revolutions of reducing sprocket 142 arerequired for one full turn of cam sprocket 140.

The portion of the driving structure between walls 22 is shown in FIGS.3 and 4, there being a feeder sprocket 146 mounted for rotation withfeeder shaft 102 and a planetary gear assembly 148 mounted for operationon planetary shaft 106. A connecting arm .150 is rigidly secured tofeeder shaft 102 adjacent feeder sprocket 146 and is pivotally coupledat the outer end thereof to a feeder crank 152 which extends upwardlyfor pivotal connection to bracket 98 of feeder 88. Thus, rotation offeeder sprocket 146 causes reciprocation of feeder crank 152, whereuponfeeder '88 pivots about pin '90 toward and away from drum 40, the throwof connecting arm 150 being set to limit inward swinging of the gatemember 92; thereby the latter closes the proximal cavity 44 as shown inFIG. 4.

The planetary gear assembly 148, shown in detail in FIG. 7, includes asun gear 154 keyed for rotation with planetary shaft 106. A pair ofplanetary gears 156 are meshed with sun gear 154 and are interconnectedby a pair of opposed arms 158 which are journalled over planetary shaft106 and have sleeves 160 extending along the shaft, one of the sleevesrigidly mounting drive sprocket 138. An outer case 162 having a toothedinner surface 164 meshing with planetary gears 156 circumscribes thelatter and has a pair of opposed side discs 166 rotatably mounted aboutsleeves 160 by collars 168.

One of the collars 168 is provided with a feeder driving sprocket .170which rotates therewith and is coupled to feeder sprocket 146 by a chain172 (FIGS. 3 and 4). Sleeves and collars 168 are thus freely rotatablewith respect to each other and also with respect to planetary shaft 106.

With reference to FIGS. 3 and 4, a brake cylinder 174, having a push rod176, is secured to one of the legs 30 by a strap 178, push rod 176 beingsecured to a depending bar 180. A brake arm 182 is rigidly secured tothe uppermost end of bar and pivotally carries, at its opposed ends, apair of brake links 184 which are pivotally mounted between Walls 22 bycorresponding pintles 186. Each link 184 has a brake shoe 188 thereon inspaced, partially circumscribing relationship to the outer surface ofcase 162. A coil spring 190 interconnects strap 180 to normally biaspush rod 176 into brake cylinder 174 whereby brake shoes 188 do notcontact outer case 162.

As shown in FIGS. 2 and 8, a lever .192 is pivotally mounted by a levershaft 193 for swinging movement parallel to walls 22 and is normallybiased upwardly by a coil spring 194 interconnecting the correspondingupper wall section 24 and bracket 196 depending from lever' 192. Avertical guide 198 extends laterally from upper wall section 24 and hasa longitudinal slot 200 formed therein for receiving lever 192. A latch202 is pivotally mounted in side-by-side relationship to guide 198, thelatch having a notch 204 formed therein for receiving lever 192.

A piston and cylinder assembly structure, broadly designated 206, ispivotally mounted on a flange 208 extending forwardly'from crossbeam 32.The cylinder 210 of the structure receives a linearly reciprocableplunger 212, the latter having a forwardly extending ram 214 whichterminates in a head 216. As is apparent from FIG. 5, ram 214 and head216 are vertically split for travel on the opposed sides of ram guide 60and divider 58. A ram crank 218 underlies plunger 212 and is rigidlysecured to lever shaft 193 for swinging movement toward and away fromram 214, there being an upstanding finger 220 on crank 218 for engagingthe ram.

Timing mechanism for machine 20 is shown schematically in FIG. 10, withthe various parts being arranged corresponding to their positions onmachine 20 as illustrated in FIG. 2. The mechanism includes a drum cam222 having a plurality of laterally extending trip pins 224 and mountedfor rotation with drum shaft 38 adjacent support plate 36 (FIG. 2). Alatch switch 226 and a solenoid switch 228 disposed in advance thereof,are mounted on drum support plate 36 for actuation by trip pins 224.Latch switch 226 is connected to a latch solenoid 230 having an armature232 pivotally connected at the uppermost end of lever latch 202 as bestshown in FIG. 8.

Solenoid switch 228 has a pair of poles A and B connected throughcorresponding leads 234 and 236 to a lever switch 238 and a relaycontrol 240. Relay control 240 is connected through line 244 to a relayunit 246 having a relay switch 248 with poles C and D. Lever switch 138,relay control 240, relay unit 246, and relay switch 248 are mountedtogether in a switching box 250 on an upper wall section 24 underlyinglever 192. Actuation of lever switch 238 and relay control 240 iseffected b y movement of a trip 253 pivotally coupled to switching box250 and engaging the lower surface of bracket 196. Trip 253 is yieldablybiased upwardly whereby the same travels upwardly and downwardly inresponse to corresponding movements of lever 1'92.

Pole D of relay switch 248 is connected through lines 252 and 254 to afirst valve solenoid 256, the energization of which causes theapplication of hydraulic pressure through a valve assembly 257 to moveplunger 212 outwardly of cylinder 210. Pole C of relay switch 248 isconnected through lead 258 to a hydraulic cam switch 260 which ismounted on a bracket 262 underlying hydraulic cam wheel 120 (FIG. 9).Switch 260 includes poles E and F which are alternately connected tolead 258 by the operation of camming ridges 124 of hydraulic cam wheel120.

Pole A of hydraulic cam switch 260 is connected through lead 264 to line254 and thereby first valve solenoid 256. Pole B is connected to asecond valve solenoid 266 through line 268, the energization of thesecond solenoid operating through valve assembly 257 to cause retractionof plunger 212 into cylinder 210.

Pole A of solenoid switch 228, in addition to being connected to leverswitch 238, is also connected through lead 234 to line 270 and thence toa brake switch 272. Brake switch 272 is mounted on bracket 262 adjacentbrake cam wheel 122 (FIG. 9) and the closing of switch 272 is controlledby camming ridge 126. Closing of brake switch 272 causes energization ofbrake solenoid 274 which, through valve mechanism 276, causes fluidoperation of brake cylinder 174 to force push rod 176 out wardly andthereby shift brake shoes 188 into engagement 'with outer case 162 ofplanetary gear assembly 148. Switches 226, 228, 238 and 248 areconnected to a power source, such as a battery, 278 throughcorresponding lines.

In operation, hay or other compressible material is continuously fedfrom a conveyor belt 280 into supply hopper 78 for precompression incavity 44a as shown in FIG. 3. During precompression, rotation of powerwheel 132 of the prime mover causes corresponding rotation of drivewheel 128 and clutch shaft 108 which, in turn, through actuation ofclutch assembly 112, causes rotation of clutch sprocket 110 for drivingouter sprocket 114. Rotation of outer sprocket 114, acting throughplanetary shaft 106, causes rotation of sun gear 154, whereuponplanetary gears 156 remain stationary with respect to planetary shaft106 due to the resistance against rotation of drum 40 caused by the haybeing fed into the loading station. Planetary gears 156 thus must rotateabout their respective axes which cause rotation of outer case 162 andconsequently feeder driving sprocket 170 rotates.

Rotation of feeder driving sprocket 170 causes corresponding rotation offeeder sprocket 146 which revolves connecting arm 150 to verticallyreciprocate feeder crank 152 and swing gate member 92 toward and awayfrom drum 40 to press the hay against the latter radially there of. Whengate members 92 is swung to a closed position over drum 40, as shown inFIG. 4, hay will be received on shelf 94, whereupon, when gate member 92swings away from drum 40, the hay upon shelf 94 is wiped off by scraperedge 96 and falls into cavity 44a for subsequent packing.

While feeder 88 is filling, shafts 102, 104, 106 and 108 all rotate torevolve the corresponding sprockets and cam wheels. The electricalswitching position are set subsequentially as shown in FIG. withsolenoid switch 228 at the B pole; latch switch 226 opens wherebysolenoid 230 is de-energized so that armature 232 will be extended topush latch 202 into holding position with notch 204 embracing lever 192to hold the latter in its lower position; lever switch 238 closed; relayswitch 248 at the C pole; cam switch 260 at the E pole; brake switch 272open with brake solenoid 274 thereby being deenergized; relay control240 open and thereby relay 246 de-energized; first valve solenoid 256energized for forcing plunger 212 outwardly for compression of the hayin cavity 44c which was filled in a preceding cycle; and second valvesolenoid 266 de-energized.

Feeder sprocket 146, through feeder shaft 102, rotates reducing sprocket142 whereby chain 144 drives cam sprocket 140 to rotate cam wheels 120and 122 through cam shaft 104. The 4:1 radius ratio of cam sprocket 140and reducing sprocket 142 results in four revolutions of feeder sprocket146 for each full turn of cam wheels and 122. One full turn of camwheels 120 and 122 represents a cycle of operation of machine 20, andthus feeder 88 swings toward and away from drum 40 four times for eachcycle. Prior to the fourth reciprocation of gate member 92, cammingridge 124 of hydraulic cam wheel 120 shifts the contact arm of camswitch 260 from pole E to pole F to simultaneously energize second valvesolenoid 256, de -energizing first valve solenoid 266. Valve assembly257 is thereby operated to retract ram 214 from cavity 440 to theposition shown in FIG. 4.

The operation of the stepping mechanism for drum 40 proceeds in thefollowing manner. Upon completion of the fourth reciprocation of gatemember 92, brake cam wheel 122 will have advanced to a position wherebycamming ridge 126 closes switch 272 which, through line 270 and switch238, receives current from battery 278 to energize solenoid 274 andthereby cause fluid operation of brake cylinder 174 to advance push rod176 to pivot brake shoes 188 into engagement with the outer surface ofcase 162 to stop rotation of the latter. When case 162 stops, there isalso discontinuance of rotation of feeding shaft 102, cam shaft 104 andthe wheels and cams thereof. Since sun gear 154 continues to rotate, andthe resistance of brake shoes 188 is greater than the resistance againstrotation of drum 40, planetary gears 156 rotate about their axes inmeshing cooperation with toothed surface 164 of case 162 and are therebycaused to revolve about planetary shaft 106 to rotate sleeves tocommence counterclockwise rotation (FIGS. 1, 3 and 4) of drum 40, drumcam 222 through drive sprocket 138, chain 139, drum sprocket 141, anddrum shaft 38.

At the start of drum rotation, switch 228 is operated by a trip pin 224to shift the contact arm thereof from pole B to pole A to complete analternate circuit from battery 278 to brake switch 272 through lead 234and line 270. After drum 40 has rotated a sufficient increment to carrythe advance lug 42 of cavity 44b by head 216 of ram 214, switch 226 isclosed by an advancing trip pin 224 to energize latch solenoid 230 whichpulls in armature 232 and thereby swings lever latch 202 from its normalholding position to permit lever 192 to swing upwardly in response tothe urging of spring 194. When lever 192 swings upwardly, it rotateslever shaft 194 which pivots ram crank 218 upwardly to raise ram 214whereby head 216 follows the inclined brace 50 into cavity 44b until theupper edge of head 216 engages rim 41 to thereby prevent advance of haypast the ram. Head 216 is inclined at its upper face to form a forwardsloping edge to facilitate travel along deflector brace 50. Ram 214 andits head 216 are maintained in proper alignment by guide 60.

As cavity 440 rotates from the material loading station adjacent gatemember 92 through the cutting station defined around knife 54, theprecompressed, elongated mass is divided into a pair of side-by-sideunits. Simultaneously, the units in cavity 441; are being compressedagainst anvil faces 46 of the advance lug 42 of cavity 44a by head 216of ram 214. The units in cavity 44b are thus initially compressed byhead 216 as drum 40 rotates, such rotation ending when a correspondingtrip pin engages switch 228 to cause shifting of the contact arm thereofto pole B which, through lead 236, relay control 240, and line 244causes energization of relay unit 246, which energization shifts thecontact arm of relay switch 248 to pole D. Current from battery 278 thuspasses through pole D, lines 252 and 254 to cause energization of firstvalve solenoid 256.

Trip pins 224 are spaced whereby rotation of drum 40 is discontinued asback-up elements 62, which have been forced down by lug 42 travelingthereabove, swing upwardly into cavity 44a behind lug 42 and engagecorresponding rear surfaces 47 thereof. Since first valve solenoid 256has been energized, plunger 212 of piston and cylinder assembly 206 willadvance to commence linear travel of ram 214 into and along cavity 441),longitudinally of the latter and tangentially of the drum, toward anvilfaces 46 of lug 42. A toroidal compression station is defined by sidewalls 22, arcuate plate 52 and rim 41 of drum 40 and assembly 206 andlugs 42 comprise condensing structure for compacting the material atsaid station.

When the contact arm of switch 228 is thrown to begin compression bypiston and cylinder assembly 206, there is a correspondingde-energization of brake solenoid 274.

since current thereto was carried through pole A of switch 228.De-energization of brake solenoid 274 operates valve mechanism 276 topermit spring 196 to retract push rod 176 to thereby shift brake shoes188 outwardly from case 162 whereby the latter commences to rotate tostart a new cycle of filling by feeder 38.

When the filling operation begins, a laterally extending roller 286 onfeeder crank 152 engages the upper surface of lever 192 upon the firstdownward reciprocation of the crank to shift lever 192 within levernotch 204 and thereby, effects relatching of lever 192. The downwardswinging of lever 192 closes switch 238 and opens relay control 240 butcam wheel 120 reshifts switch 265 to pole E to sustain energization offirst valve solenoid 256. Swinging of lever 192 causes a correspondinglowering of ram crank 218, but ram 214 is within the compression chamberand, therefore, will not drop down.

While feeder 88 is filling cavity 44:? which has ad vanced to theloading station, ram 214 is being forced against the units within cavity44b until a preset pressure is reached, at which time ram 214 dwellsagainst the units. Compression within the compressing station issubstantially perpendicular to the packing force of feeder 88 wherebymaximum density is obtained to form the final hay wafers 284. The linearforce of ram 214 is borne primarily by backup elements 62 as they engagerear faces 47 of lug 42. This protects against breaking or weakening of.the lugs. Ram 214- is then retracted as explained before, When thecamming ridge 124 of hydraulic cam wheel 120 has rotated to a properposition to cause movement of the contact arm of switch 260. Switch 260is shifted to the B pole to de-energize first valve solenoid 256 andsimultaneously energize second valve solenoid 266 which effectsretraction of ram 214, the latter dropping down to finger 220 which waspreviously lowered.

Thus, as outer case 162 rotates, there will be simultaneous action offeeder 8S and ram 214 in corresponding cavities 44, with drum 40remaining stationary. When outer case 162 is engaged by brake shoes 188,feeder 83 discontinues reciprocation while simultaneously drum iiibeings to rotate. The drive assembly for the machine therefore, operatesas a stepping mechanism to advance the cavities successively past theloading, cutting and compressing stations. During rotation of drum 49there is no reciprocation of ram 214, although the latter is raised at apredetermined time to begin compression of the advancing sliced units.Advance of ram 214 begins only when drum 40 stops rotating, thuspermitting insertion of a backup means to protect against high pressuresbeing placed directly on the lugs, whereby the latter will not becomeweakened over a prolonged period of use, and also to hold drum 4%against retrograde rotation during compression of the units.

The valve system for piston and cylinder assembly 206 is arranged todeliver a continuous pressure to plunger 212 for a predetermined periodof time during each dwell in the rotations of drum 46, whereby thedensity of the wafers formed in the compressing station is substantiallyuniform even if hay is delivered at a nonuniform rate to hopper 78.Thus, whether a large or small amount of hay is received by a cavity 44,the same pressure will be impressed thereon in the compression stationwith the final wafers varying in size corresponding to the original haypacked by feeder 88.

The sequential steps performed on a particular wafer 284 by machine 20thus may be summarized as follows: hay or other compressible material isgathered into an elongated mass in cavity 44a at the loading station andpacked by a compressive force applied by feeder 88 radially(substantially transversely) of the mass, with the gathering and packingbeing simultaneous and inter mittent as feeder crank 152 reciprocates toadd hay following each application of packing force; after packing, themass in cavity 44a is pushed at one end thereof by a lug 42along an'arcuate path of travel about drum 40 into a cutting station where themass is severed longitudinally into a pair of side-by-side units; themass then continues on its arcuate path into a compressing station orzone where it is held against longitudinal movement by backup elements62, against lateral movement by walls 22, and against radial movement byrim 41 and plate 52; after the mass comes to rest in the zone, ram 214applies a longitudinal compressive force on the other end of the massina lineal direction tangential to the arcuate path of the'mass, themass being condensed into a wafer by achieving a predetermined pressureand by application of longitudinal pressure to the wafer for a presetperiod of time, whereupon the ram is retracted to release thelongitudinal compressive force.

The rotary action, of course, provides continuous operation as the hayis gathered into successive, elongated masses in cavities Mia-44c. Thecavities successively communicate with hopper 78, and while one cavityis being packed by feeder 88, the hay in the next preceding cavity issubdivided by knife 54 and the units are being compressed in yet a thirdcavity, the latter being backed up by elements 62 in the next precedingcavity.

Many adjustments may be made in machine 20 to adapt it for hay or othermaterial with varying moisture and fiber content, state of comminution,and fusing characteristics. For example, the 4:1 ratio between camsprocket and reducer sprocket 142 may be changed to vary the number offilling reciprocations of feeder 88 for each cavity. The time of dwellmay be varied on the application of force by ram 214- by altering thecamming ridges on the cam wheels. In this regard, the ridges may beformed of a plurality of side-by-side removable units which can beselectively removed or added to vary the arc length of the ridge andthereby vary the time period of pressure application. It should also benoted that better results have been obtained with chopped hay serving asthe original feed.

It will be appreciated that a field machine would probably have a drumwith a wider rim so that a row of lugs 42 may be provided to form aplurality of wafers simultaneously. Each lug 42 would have acorresponding split ram 214 to effect the compression operation.

Having thus described the invention, what is claimed as new and desiredto be secured by Letters Patent is:

1. A wafering machine comprising:

a rotor having lug means at its periphery, presenting an elongatedcavity extending circumferentially of the rotor;

a material loading station adjacent said periphery;

a material compressing station adjacent said periphery in advance of theloading station with respect to the direction of rotation of the rotor;

stepping mechanism coupled with the rotor for rotating the latter stepby step to advance the cavity successively past said stations;

a feeder at said loading station for filling the cavity with saidmaterials; and

structure at said compressing station, movable between each step ofrotative advancement of the rotor, into and along the cavity,longitudinally of the latter and tangentially of the rotor, forcondensing the material against said lug means.

2. The invention of claim 1; and

a backup for said lug means movable to a position therebehindimmediately prior to each operation of said structure.

3. The invention of claim 1,

said feeder having means for packing the material into the cavity.

4. The invention of claim 1,

there being means interconnecting said mechanism and the rotor forholding the latter against rotation during filling of the cavity withmaterial by said feeder.

5. The invention of claim 1,

there being a plurality of lug means, presenting a number of cavitieswhereby, during each operation of said structure within a cavity, saidfeeder operates to fill another of the cavities.

6. The invention of claim 5,

and a backup for said lug means movable to a position therebehind intostill another of said cavities immediately prior to each operation ofsaid structure.

7. The invention of claim 1,

said structure including a reciprocable ram having means for exerting asteady pressure on the material for a predetermined period of timeduring each dwell in the rotation of the rotor.

8. The invention of claim 7,

said structure having means for reciprocating the ram along asubstantially linear path of travel.

9. The invention of claim 1,

and a knife means within the path of travel of the material in thecavity from the loading station to the compressing station forsubdividing the material into a number of separate units.

10. The invention of claim 3,

said feeder including a member movable toward and away from the rotor topress the material against 1 the latter radially thereof.

11. The invention of claim 10,

and a material supply hopper communicating with the cavity when thelatter is adjacent the loading station, said member operating within thehopper.

12.. A wafer machine comprising:

a rotor having a plurality of outwardly extending lugs, presenting anumber of elongated, circumferential, material-receiving cavities;

a material supply hopper disposed for successive communication with thecavities during rotation of the rotor;

a feeder swingable within the hopper toward and away from the rotor forpacking the material into the cavities radially of the rotor when thecavities are in communication with the hopper;

knife means in advance of the feeder within the path of travel of thematerial in the cavities for subdividing the material into a number ofseparate units;

a fluid piston and cylinder assembly, in advance of said knife means,having a reciprocable ram movable into the path of travel of said unitsfor compressing the latter;

stepping mechanism coupled with said rotor for intermittent rotativeadvancement of the latter whereby, during each dwell in rotoradvancement, material is packed into one cavity, the material issubdivided in the next preceding cavity and units are compressed in athird cavity;

a lug backup element movable into said next preceding cavity during eachof said dwells for holding the rotor against retrograde rotation duringcompression of the units by the ram; and

means coupled with said assembly for shifting the ram into said thirdcavity prior to each compressing movement of the ram longitudinally ofthe third cavity, tangentially of the rotor, and toward the lug beingbacked up by said element.

13. The method of wafering a compressible material comprising:

gathering the material together into an elongated mass;

applying a compressive force on the mass transversely thereof;

pushing on one end of the transversely compressed mass to shift the sameinto a Zone for further handling;

holding the elongated mass against lateral movement while in said zone;

holding said mass at said one end of the latter against longitudinalmovement of the mass from within said zone;

applying a compressive force on said transversely compressed mass at theopposite end thereof toward said one end by a moving member to initiallycompress said mass while it is being shifted to said zone to condensethe mass longitudinally thereof; and

continuing the application of said longitudinal force on said mass untila predetermined pressure has been exerted thereon.

14. The invention of claim 13:

and releasing said longitudinal compressive force from said mass afterthe latter has been held for a period of time at said predeterminedpressure.

15. The invention of claim 13; and

severing the elongated, transversely compressed mass longitudinallythereof into a plurality of side-by-side units prior to the applicationof said longitudinal force.

16. The invention of claim 15, and

severing into said units while the transversely compressed mass is beingshifted to said zone.

17. The invention of claim 13,

said gathering of the material and said application of transverse forcesbeing simultaneous and intermittent whereby additional material is addedfollowing each application of the transverse force.

18. The invention of claim 13, and

gathering the material together into successive elongated masses andapplying transverse compressive force thereto during longitudinalcompression of each preceding, transversely compressed mass.

19. The invention of claim 13,

said pushing being along an arcuate path of travel, said application oflongitudinal compressive force being lineal and tangential to said path.

20. The invention of claim 19, and

holding the mass during pushing against lateral movement and againstmovement radially of said path.

References Cited UNITED STATES PATENTS 3,070,002 12/1962 Mathews l00-35WALTER A. SCHEEL, Primary Examiner.

JOSEPH SHEA, Assistant Examiner.

U.S. Cl. X.R.

